CN221144759U

CN221144759U - Rotary compressor and refrigeration equipment

Info

Publication number: CN221144759U
Application number: CN202323266191.XU
Authority: CN
Inventors: 赵庆富; 潘雯; 李选平
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2023-11-30
Filing date: 2023-11-30
Publication date: 2024-06-14
Anticipated expiration: 2033-11-30

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, wherein the rotary compressor comprises a pump body component, a motor component, a crankshaft and a bearing body, and the pump body component comprises a cylinder; the motor assembly includes a stator and a rotor, the stator being disposed about the rotor; the crankshaft penetrates through the rotor and is connected with the rotor, the crankshaft comprises an eccentric part and a connecting section, the eccentric part and the connecting section are respectively positioned at two ends of the motor assembly along the axial direction of the crankshaft, the eccentric part is rotationally arranged in the cylinder, the crankshaft is provided with a central oil hole, the connecting section is provided with a first oil outlet hole, and the first oil outlet hole is communicated with the central oil hole; the bearing body is provided with a shaft hole, and the bearing body is sleeved on the connecting section through the shaft hole; wherein, the play oil end of first oil outlet is towards the gap between the outer peripheral wall of linkage segment and the inner wall in shaft hole. The bearing body and the crankshaft of the rotary compressor have good lubricity and small abrasion.

Description

Rotary compressor and refrigeration equipment

Technical Field

The utility model relates to the technical field of compressors, in particular to a rotary compressor and refrigeration equipment.

Background

With the use of high-speed, high-efficiency and high-product-thickness motors in specific environments, ensuring the coaxiality of the stator and rotor of the motor in the running process and reducing the shaft end deformation of the crankshaft become important to ensure the reliability of the rotary compressor. For this purpose, the partially rotary compressor achieves the above object by installing a motor bearing at an end of the motor. However, when the conventional sliding bearing is used as a motor bearing, the motor bearing is easy to wear, and the reliability is relatively poor, so that the reliability of the whole rotary compressor is affected.

Disclosure of utility model

The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides the rotary compressor with good lubricity and small abrasion between the bearing body and the crankshaft.

The utility model also provides refrigeration equipment with the rotary compressor.

An embodiment of a rotary compressor according to a first aspect of the present utility model includes: the pump body assembly comprises a cylinder; an electric machine assembly comprising a stator and a rotor, the stator being arranged around the rotor; the crankshaft penetrates through the rotor and is connected with the rotor, the crankshaft comprises an eccentric part and a connecting section, the eccentric part and the connecting section are respectively positioned at two ends of the motor assembly along the axial direction of the crankshaft, the eccentric part is rotationally arranged in the cylinder, the crankshaft is provided with a central oil hole, the connecting section is provided with a first oil outlet, and the first oil outlet is communicated with the central oil hole; the bearing body is provided with a shaft hole, and the bearing body is sleeved on the connecting section through the shaft hole; the oil outlet end of the first oil outlet hole faces to a gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole.

The rotary compressor according to the embodiment of the first aspect of the utility model has at least the following advantages: through setting up the first oil outlet that communicates with the centre oilhole at the linkage segment of bent axle to gap between the inner wall in the shaft hole of first oil outlet orientation linkage segment's peripheral wall and bearing body, when rotary compressor operates, lubricating oil can directly flow to between the inner wall in linkage segment and shaft hole through centre oilhole and first oil outlet, increase the oil film thickness between the inner wall in linkage segment and shaft hole, reach lubricated purpose, make and remain good lubrication state throughout between bent axle and the bearing body, reduce the wearing and tearing of bent axle and bearing body, effectively improve bearing body and rotary compressor's reliability. Meanwhile, part of lubricating oil flows out from the first oil outlet, so that the oil quantity reaching the top space of the crankshaft can be reduced, the oil discharge quantity of the rotary compressor is reduced, and the reliability of the rotary compressor is further improved.

According to some embodiments of the utility model, the first oil outlet hole is arranged along a radial direction of the crankshaft.

According to some embodiments of the utility model, the outer peripheral wall of the connecting section is provided with a groove body, the groove body is communicated with the first oil outlet, and an oil groove is defined between the groove body and the inner wall of the shaft hole.

According to some embodiments of the utility model, the groove body includes a bottom wall and a side wall, the side wall is connected to one end of the bottom wall in the axial direction of the crankshaft, the bottom wall is closer to the central axis of the crankshaft than the side wall, and both ends of the bottom wall in the circumferential direction of the crankshaft extend to the outer peripheral wall of the connecting section, respectively.

According to some embodiments of the utility model, the bottom wall is a straight wall, and an angle θ between a reference plane passing through a central axis of the crankshaft and perpendicular to the bottom wall and a deflection direction of the eccentric portion is as follows: θ is more than or equal to 45 degrees and less than or equal to 135 degrees.

According to some embodiments of the utility model, the maximum radial dimension of the connecting section is D, and the maximum linear distance between two ends of the groove body in the circumferential direction of the crankshaft is W, so that: W/D is less than or equal to 0.7.

According to some embodiments of the utility model, an end of the groove body, which faces the motor assembly, penetrates through the connecting section along the axial direction of the crankshaft, and the connecting section comprises a first oil blocking part which is positioned at the other end of the groove body.

According to some embodiments of the utility model, the length of the first oil blocking portion is L ₁, and the maximum length of the groove body is L ₂ along the axial direction of the crankshaft, which satisfies the following conditions: l ₁/L₂ is more than or equal to 0.25.

According to some embodiments of the utility model, the connecting section includes a first oil blocking portion and a second oil blocking portion, and the first oil blocking portion and the second oil blocking portion are respectively located at two ends of the groove body along an axial direction of the crankshaft.

According to some embodiments of the utility model, the central oil hole is closed towards one end of the bearing body.

According to some embodiments of the utility model, a second oil outlet is arranged at one end of the connecting section, which is away from the motor assembly, the second oil outlet is communicated with the central oil hole, an oil outlet end of the second oil outlet is positioned on the upper end wall of the connecting section, and the inner diameter of the second oil outlet is smaller than the inner diameter of the first oil outlet and the inner diameter of the central oil hole.

A refrigeration appliance according to an embodiment of the second aspect of the utility model comprises a rotary compressor according to an embodiment of the first aspect of the utility model.

The refrigerating equipment according to the embodiment of the second aspect of the utility model has at least the following beneficial effects: by adopting the rotary compressor, the first oil outlet communicated with the central oil hole is formed in the connecting section of the crankshaft, and the first oil outlet faces the gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole of the bearing body. Meanwhile, part of lubricating oil flows out from the first oil outlet, so that the oil quantity reaching the top space of the crankshaft can be reduced, the oil discharge quantity of the rotary compressor is reduced, and the reliability of the rotary compressor is further improved.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The utility model is further described with reference to the accompanying drawings and examples, in which:

FIG. 1 is a schematic cross-sectional view showing an internal structure of a rotary compressor in accordance with an embodiment of the present utility model;

Fig. 2 is an enlarged view at a in fig. 1;

FIG. 3 is a front view of a crankshaft in an embodiment of the present utility model;

FIG. 4 is a cross-sectional view taken at B-B in FIG. 3;

FIG. 5 is a partial schematic view of a crankshaft in accordance with another embodiment of the present utility model;

FIG. 6 is a partial cross-sectional view of a crankshaft in another embodiment of the present utility model;

FIG. 7 is a graph showing the thickness of oil film as a function of angle θ in an embodiment of the present utility model;

FIG. 8 is a graph showing the variation of the oil film thickness with the variation of the ratio W/D in the embodiment of the present utility model;

FIG. 9 is a graph showing the variation of the oil film thickness with the variation of the ratio L ₁/L₂ in the example of the present utility model.

Reference numerals:

A pump body assembly 100; a first cylinder 110; a first compression chamber 111; a first roller 112; a second cylinder 120; a second compression chamber 121; a second roller 122; a first bearing 130; a second bearing 140; a partition 150;

a motor assembly 200; a stator 210; a rotor 220; a balance weight 221;

A crankshaft 300; a eccentric portion 310; a connecting section 320; a first oil outlet hole 321; a second oil outlet hole 322; a tank 323; a first oil baffle 324; a second oil baffle 325; a bottom wall 326; a center oil hole 330; an oil groove 340;

a bearing body 400; a main body 410; a mounting portion 420; shaft hole 430.

Detailed Description

Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.

In the description of the present utility model, it should be understood that references to orientation descriptions such as upper, lower, front, rear, left, right, etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience of description of the present utility model and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present utility model.

In the description of the present utility model, a number means one or more, a number means two or more, and greater than, less than, exceeding, etc. are understood to not include the present number, and above, below, within, etc. are understood to include the present number. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, mounting, connection, assembly, cooperation, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical solution.

With the use of high-speed, high-efficiency and high-product-thickness motors in specific environments, ensuring the coaxiality of the stator and rotor of the motor in the running process and reducing the shaft end deformation of the crankshaft become important to ensure the reliability of the rotary compressor. For this purpose, the partially rotary compressor achieves the above object by installing a motor bearing at an end of the motor.

However, when the conventional sliding bearing is used as a motor bearing, on one hand, the motor bearing is easy to wear, and the reliability is relatively poor; on the other hand, by means of the lubricating oil sprayed to the top space of the crankshaft flowing into the gap between the crankshaft and the motor bearing under the action of gravity, the amount of the lubricating oil in the gap is small, the thickness of an oil film is small, the lubricating performance in a high-speed running state is difficult to meet, the abrasion of the crankshaft and the motor bearing is aggravated, the service life and the reliability of the motor bearing are affected, and the reliability of the whole machine of the rotary compressor is further affected.

To this end, referring to fig. 1 to 6, a first aspect of the embodiment of the present utility model provides a rotary compressor, which may be a single-cylinder rotary compressor or a double-cylinder rotary compressor.

Referring to fig. 1, a schematic cross-sectional view of an internal structure of a rotary compressor is shown, with a housing omitted. It will be appreciated that the rotary compressor includes a pump body assembly 100, a motor assembly 200, a crankshaft 300, and a bearing body 400. The pump body assembly 100 is of a double-cylinder structure, specifically, the pump body assembly 100 includes a first cylinder 110 and a second cylinder 120, the pump body assembly 100 further includes a first bearing 130, a second bearing 140 and a partition 150, the first cylinder 110 is disposed on the upper side of the second cylinder 120, the partition 150 is sandwiched between the first cylinder 110 and the second cylinder 120, the first bearing 130 is disposed on the upper side of the first cylinder 110, and the second bearing 140 is disposed on the lower side of the second cylinder 120, that is, the first cylinder 110 and the second cylinder 120 are disposed between the first bearing 130 and the second bearing 140. The first cylinder 110 is provided with a first compression chamber 111 and a first roller 112 installed in the first compression chamber 111, and similarly, the second cylinder 120 is provided with a second compression chamber 121 and a second roller 122 installed in the second compression chamber 121. The lower portion of the crankshaft 300 sequentially passes through the first bearing 130, the first cylinder 110, the partition 150, the second cylinder 120, and the second bearing 140, and the lower portion of the crankshaft 300 is provided with two eccentric portions 310, the eccentric directions of which are different, for example, the eccentric directions of the two eccentric portions 310 are opposite, and the eccentric direction of the eccentric portion 310 is a direction from the central axis of the crankshaft 300 toward the center of the eccentric portion 310. The two eccentric portions 310 are disposed at an interval up and down and rotatably disposed in the first compression chamber 111 and the second compression chamber 121, respectively, thereby realizing connection of the crankshaft 300 with the first cylinder 110 and connection of the crankshaft 300 with the second cylinder 120.

Referring to fig. 1, it can be appreciated that by providing the first bearing 130 and the second bearing 140, the crankshaft 300 is supported and positioned to bear the reaction force of the compressed gas in the first cylinder 110 and the second cylinder 120 during the operation of the rotary compressor, and to improve the operation stability of the first cylinder 110 and the second cylinder 120.

Referring to fig. 1, it can be appreciated that the motor assembly 200 is connected with the crankshaft 300 and is located above the pump body assembly 100, and specifically, the motor assembly 200 includes a stator 210 and a rotor 220, generally speaking, the stator 210 is fixedly connected with a housing of a rotary compressor, the stator 210 is in a ring shape, the rotor 220 is disposed in an inner ring of the stator 210, that is, the stator 210 is disposed around the rotor 220, and the crankshaft 300 is disposed through the rotor 220 and is fixedly connected with the rotor 220. The rotor 220 can rotate relative to the stator 210, and under the action of the magnetic field, the rotor 220 can be driven to rotate relative to the stator 210, so that the rotor 220 drives the eccentric part 310 to rotate through the crankshaft 300, and the refrigerant is compressed in the first compression cavity 111 and the second compression cavity 121.

Referring to fig. 1, it can be understood that, in order to balance the centrifugal force of the eccentric portion 310 of the crankshaft 300, the weights 221 are mounted at both upper and lower ends of the rotor 220, and the two weights 221 at both upper and lower ends are located at both ends of the rotor 220 in the radial direction, that is, the two weights 221 are disposed opposite to each other. Therefore, the balance of the rotor 220 in the rotation process can be improved, the radial offset of the rotor 220 can be reduced, the coaxiality of the stator 210 and the rotor 220 can be improved, and the dynamic and static balance effect can be improved.

Referring to fig. 1, it can be understood that, in order to improve the coaxiality of the stator 210 and the rotor 220, to prevent the stator 210 from being scratched with the rotor 220 and to reduce the deflection of the end of the crankshaft 300, the bearing body 400 is mounted on the upper end of the crankshaft 300, i.e., the bearing body 400 is located at the side of the rotor 220 facing away from the pump body assembly 100.

Referring to fig. 1, it can be understood that, specifically, the bearing body 400 includes a main body part 410 and a mounting part 420, the main body part 410 has a cylindrical shape, the mounting part 420 is connected to an upper end of the main body part 410 and has a circular ring shape, the mounting part 420 is disposed around the main body part 410, and the bearing body 400 can be fixedly mounted through the mounting part 420. The body portion 410 and the mounting portion 420 are integrally formed, and are easy to manufacture.

Referring to fig. 1 and 2, it can be understood that the body part 410 is provided with a shaft hole 430, and the shaft hole 430 penetrates the body part 410 in the axial direction of the bearing body 400. Correspondingly, the crankshaft 300 includes a connecting section 320, the connecting section 320 is located at the upper end of the crankshaft 300, and the connecting section 320 has a cylindrical structure. The bearing body 400 is sleeved on the connecting section 320 through the shaft hole 430, so that the crankshaft 300 is supported and positioned. Generally, connecting section 320 is fully received within shaft bore 430.

Referring to fig. 1 and 2, it can be appreciated that the crankshaft 300 is provided with a central oil hole 330, and the central oil hole 330 extends from bottom to top to the connecting section 320 in the axial direction of the crankshaft 300. Generally, an oil sump is provided in a housing of the rotary compressor, for storing lubricating oil, and is located below the pump body assembly 100, and the lower end of the central oil hole 330 is opened and communicates with the oil groove 340. When the rotary compressor is operated, the crankshaft 300 rotates at a high speed, a continuous oil-feeding state is formed in the central oil hole 330, so that lubricating oil in the oil sump is conveyed upwards through the central oil hole 330, the pump body assembly 100, the crankshaft 300 and the like are lubricated, abrasion is reduced, part of heat generated in the rotation process of the crankshaft 300 can be taken away through the lubricating oil, and the reliability of the rotary compressor is improved.

Referring to fig. 2, it can be appreciated that the connection section 320 is provided with the first oil outlet holes 321, and the first oil outlet holes 321 are arranged along the radial direction of the connection section 320, thereby facilitating the processing. One end of the first oil outlet hole 321 communicates with the central oil hole 330, and the other end (i.e., the oil outlet end of the first oil outlet hole 321) faces the gap between the outer circumferential wall of the connection section 320 and the inner wall of the shaft hole 430, that is, the oil outlet end of the first oil outlet hole 321 communicates with the gap between the outer circumferential wall of the connection section 320 and the inner wall of the shaft hole 430. Accordingly, the lubricating oil can directly flow into the gap between the outer circumferential wall of the connecting section 320 and the inner wall of the shaft hole 430 through the central oil hole 330 and the first oil outlet 321, thereby providing lubrication to the contact area of the crankshaft 300 and the bearing body 400, increasing the amount of the lubricating oil in the gap, increasing the minimum oil film thickness of the contact area, and enhancing the lubrication effect to reduce the wear of the crankshaft 300 and the bearing body 400.

It will be readily appreciated that the lubricating oil in the gap between the outer circumferential wall of the connecting section 320 and the inner wall of the shaft hole 430 will flow downward out of the gap under the action of gravity, so that the lubricating oil in the gap is in a flowing state, and thus the lubricating oil can take away part of heat generated during the rotation of the crankshaft 300 to a certain extent, so as to improve the reliability of the crankshaft 300 and the bearing body 400 and further reduce wear.

Of course, it is understood that the first oil outlet hole 321 may be disposed obliquely upward or downward as long as one end of the first oil outlet hole 321 communicates with the central oil hole 330 and the other end faces the gap between the outer circumferential wall of the connection section 320 and the inner wall of the shaft hole 430.

Through setting up the first oil outlet 321 that communicates with the central oil hole 330 at the linkage segment 320 of bent axle 300 to first oil outlet 321 is towards the gap between the outer peripheral wall of linkage segment 320 and the inner wall of shaft hole 430, and when rotary compressor was operated, lubricating oil can flow directly between the inner wall of linkage segment 320 and shaft hole 430 through central oil hole 330 and first oil outlet 321, increases the oil film thickness between the inner wall of linkage segment 320 and shaft hole 430, reaches lubricated purpose, makes between bent axle 300 and the bearing body 400 keep good lubrication state all the time, reduces the wearing and tearing of bent axle 300 and bearing body 400, effectively improves the reliability of bearing body 400 and rotary compressor. Meanwhile, since a part of the lubricating oil flows out from the first oil outlet 321, the amount of oil reaching the head space of the crankshaft 300 can be reduced to reduce the oil discharge amount of the rotary compressor, further improving the reliability of the rotary compressor.

As can be understood from the description of fig. 2 and 3, the outer peripheral wall of the connecting section 320 is provided with a groove 323, specifically, the groove 323 is a groove structure formed by cutting out a partial structure on the outer side of the connecting section 320, and the groove 323 is recessed toward the central axis of the crankshaft 300 with respect to the outer peripheral wall of the connecting section 320. The groove 323 is located at the oil outlet end of the first oil outlet hole 321, and thus, the groove 323 communicates with the first oil outlet hole 321. And, a space defined between the groove 323 and the inner wall of the shaft hole 430 forms the oil groove 340. Therefore, during the rotation of the crankshaft 300, a certain amount of lubricating oil can be always stored in the oil groove 340, so that the minimum oil film thickness between the connecting section 320 and the inner wall of the shaft hole 430 can be further increased, a good lubrication state can be always maintained between the crankshaft 300 and the bearing body 400, abrasion is reduced, and reliability of the crankshaft 300 and the bearing body 400 is greatly improved.

Referring to fig. 2 and 3, it will be appreciated that the groove 323 includes a bottom wall 326 and a side wall, the bottom wall 326 being straight and parallel to the central axis of the crankshaft 300. Along the circumference of the crankshaft 300, two ends of the bottom wall 326 respectively extend to the outer circumferential wall of the connecting section 320, namely, the bottom wall 326 is connected with the outer circumferential wall of the connecting section 320, and an edge is formed at the connection part of the bottom wall 326 and the outer circumferential wall of the connecting section 320 and is arranged along the axial direction of the crankshaft 300. Along the axial direction of the crankshaft 300, the lower end of the bottom wall 326 extends to the lower end of the connecting section 320, i.e., the lower end of the groove 323 (i.e., the end facing the motor assembly 200) penetrates the connecting section 320, the side wall is connected to the upper end of the bottom wall 326 and is perpendicular to the central axis of the crankshaft 300, i.e., the bottom wall 326 is closer to the central axis of the crankshaft 300 than the side wall, and the bottom wall 326 is rectangular. Therefore, the connection section 320 forms a first oil blocking portion 324 at the upper end of the groove 323, and the first oil blocking portion 324 protrudes relative to the bottom wall 326, such that the upper end of the groove 323 does not penetrate the connection section 320. The outer peripheral wall of the connecting section 320 at the first oil blocking portion 324 is a complete cylindrical surface, and the connecting section 320 includes a shaft section where the groove 323 is located and a shaft section where the first oil blocking portion 324 is located.

Accordingly, the oil groove 340 defined by the groove 323 and the inner wall of the shaft hole 430 is open at the lower end and provided with the first oil blocking portion 324 at the upper end. When the lubricating oil flows to the oil groove 340, the first oil blocking portion 324 may block the lubricating oil from flowing upward, so that the amount of oil reaching the head space of the crankshaft 300 may be reduced to reduce the oil discharge amount of the rotary compressor. Meanwhile, the lubricating oil mainly flows downwards through the opening, so that on one hand, the oil yield of the first oil outlet 321 can be increased, the lubrication of the crankshaft 300 and the bearing body 400 is kept, the minimum oil film thickness is increased, the abrasion is reduced, and on the other hand, the flow speed of the lubricating oil can be increased, the lubricating oil can rapidly take away heat generated in the rotating process of the crankshaft 300, and the abrasion is further reduced.

Referring to table 1, it is easy to understand that in the first example, the upper and lower ends of the groove 323 penetrate the connecting section 320, i.e., the upper and lower ends of the oil groove 340 are opened, and the minimum oil film thickness between the crankshaft 300 and the bearing body 400 is 0.701 μm; in the second example, the lower end of the groove 323 penetrates the connecting section 320, and the upper end thereof is provided with the first oil blocking portion 324, that is, the oil groove 340 is only opened at the lower end, and at this time, the minimum oil film thickness between the crankshaft 300 and the bearing body 400 is 0.883 μm, which is greater than that in the first example. Therefore, by providing the first oil blocking portion 324, the minimum oil film thickness between the crankshaft 300 and the bearing body 400 can be effectively increased.

Table 1: minimum oil film thickness contrast under different scenarios

Example	Scheme for the production of a semiconductor device	Minimum oil film thickness/. Mu.m
			A first part	The upper and lower ends of the groove body are all penetrated through the connecting section	0.701
Two (II)	The lower end of the groove body penetrates through the connecting section, and the upper end of the groove body is provided with a first oil blocking part	0.883

It will be appreciated that when the crankshaft 300 rotates and drives the eccentric portion 310 to rotate to compress the refrigerant, a side of the crankshaft 300 facing the eccentric portion 310 is a bearing side in a radial direction of the crankshaft 300. In general, the thickness of the oil film of crankshaft 300 at the load-bearing side is minimal because the load borne by the load-bearing side is greatest. When the groove 323 is provided, the bearing area of the side of the crankshaft 300 on which the groove 323 is located is small. When the groove 323 is located on the bearing side, the bearing area of the crankshaft 300 on the bearing side is reduced, the surface pressure is increased under the condition of unchanged load, the oil film thickness of the crankshaft 300 on the bearing side is further reduced, and the oil film is ultrathin, so that abrasion is increased. As the groove 323 comes closer to the bearing side, the larger the load on the crankshaft 300 on the side where the groove 323 is located in the radial direction of the crankshaft 300, the larger the surface pressure, the smaller the oil film thickness, i.e., the oil film thickness deteriorates.

Referring to fig. 3 and 4, it can be understood that the crankshaft 300 includes two eccentric portions 310, and the eccentric directions of the two eccentric portions 310 are opposite, that is, the direction of deflection is the direction from the central axis of the crankshaft 300 toward the center of the eccentric portion 310. In actual operation, when the crankshaft 300 rotates, centrifugal forces acting on the two eccentric portions 310 are generally not equal, and therefore, the sides of the crankshaft 300 facing the two eccentric portions 310 are both load-bearing sides in the radial direction of the crankshaft 300.

As can be understood from the description of fig. 3 and 4, for this purpose, a reference plane is defined which passes through the central axis of the crankshaft 300 and is perpendicular to the bottom wall 326 of the groove 323, and which has an angle θ with respect to the eccentric direction of one of the eccentric portions 310, satisfying: θ is more than or equal to 45 degrees and less than or equal to 135 degrees. Since the eccentric directions of the two eccentric portions 310 are opposite, the angle between the reference plane and the deflection direction of the other eccentric portion 310 is also satisfied in a range of greater than or equal to 45 ° and less than or equal to 135 °. When θ is smaller than 45 °, the distance between the groove 323 and the bearing side of the corresponding eccentric portion 310 is relatively short, the load borne by the side of the groove 323 on the crankshaft 300 is relatively large along the radial direction of the crankshaft 300, the surface pressure is increased, the oil film thickness is reduced, that is, the oil film thickness is deteriorated, particularly, the oil film thickness at the edge is smaller, and the abrasion is increased. When θ > 135 °, the distance between the groove 323 and the bearing side of the other eccentric portion 310 is relatively short, and similarly, along the radial direction of the crankshaft 300, the load borne by the side of the crankshaft 300 where the groove 323 is located is relatively large, the surface pressure is increased, and the oil film thickness is reduced, that is, the oil film thickness is deteriorated, particularly, the oil film thickness at the edge is smaller, which also causes the abrasion to be increased.

Referring to fig. 7, it can be understood that, under the same working condition, as the included angle θ between the reference plane and the eccentric direction of one of the eccentric portions 310 increases, the thickness of the oil film on the side of the groove 323 of the crankshaft 300 increases and then decreases along the radial direction of the crankshaft 300. When θ is equal to or greater than 45 ° and equal to or less than 135 °, the oil film thickness on the side of the groove 323 on the crankshaft 300 is equal to or greater than 1.7 μm, and when θ is less than 45 ° or θ is greater than 135 °, the oil film thickness on the side of the groove 323 on the crankshaft 300 is less than 1.7 μm. Therefore, by setting θ to 45 ° or more and θ to 135 °, for example, θ=60°, θ=90°, θ=120°, or the like, it is possible to avoid the groove 323 from being too close to any one of the bearing sides where the two eccentric portions 310 are located, thereby reducing the load to which the groove 323 is located on the crankshaft 300, reducing the surface pressure, increasing the oil film thickness at this point, and maintaining the oil film thickness stable, and further maintaining good lubricity between the crankshaft 300 and the bearing body 400, reducing wear, and improving reliability.

Referring to fig. 4, it can be understood that when θ=90°, the distance between the groove 323 and the bearing side of the two eccentric portions 310 is equal, and the distance is the largest, and at this time, the load borne by the side of the crankshaft 300 on which the groove 323 is located is the smallest, so that the thickness of the oil film can be effectively increased.

Referring to fig. 3, it can be understood that the maximum radial dimension of the connecting section 320 is defined as D, that is, the maximum outer diameter of the connecting section 320 is defined as D, the maximum linear distance of the two ends of the groove 323 in the circumferential direction of the crankshaft 300 is defined as W, that is, the linear distance of the two ends of the bottom wall 326 in the circumferential direction of the crankshaft 300 is defined as W, and that the width of the groove 323 is defined as W, so as to satisfy the following conditions: W/D is less than or equal to 0.7. Under the condition that the outer diameter D of the connecting section 320 is constant, when W/D is more than 0.7, the width W of the groove body 323 is increased, on one hand, the distance between the groove body 323 and the bearing side where the two eccentric parts 310 are positioned is shortened, particularly the distance between the edges of the two ends of the groove body 323 along the circumferential direction of the crankshaft 300 and the bearing side is shortened, the load born by the side where the groove body 323 is positioned on the crankshaft 300 is larger, the surface pressure is increased, and the thickness of an oil film at the position is reduced; on the other hand, the bearing area of the crankshaft 300 is reduced, the surface pressure is increased, and the oil film thickness is also reduced; meanwhile, along the direction perpendicular to the bottom wall 326, the depth t of the groove 323 increases, the structural rigidity of the connection section 320 decreases, the connection section 320 is easily deformed, the supporting force of the bearing body 400 to the connection section 320 is insufficient, the reliability of the rotary compressor is affected, and abnormal wear may be caused.

Referring to FIG. 8, it will be appreciated that, under the same conditions, as the ratio W/D increases, the oil film thickness on the side of crankshaft 300 where groove 323 is located decreases. When the W/D is smaller than or equal to 0.7, the thickness of the oil film is kept to be 2 mu m or more, and when the W/D is larger than 0.7, the thickness of the oil film is smaller than 2 mu m. Therefore, the W/D is not more than 0.7, and the groove 323 is provided to increase lubricity, so that the width of the groove 323 is not excessively large, and the thickness of the oil film on the side of the groove 323 on the crankshaft 300 is large, so that good lubricity is maintained between the crankshaft 300 and the bearing body 400, and abrasion is reduced. At the same time, the structural rigidity of the connection section 320 can be ensured to meet the requirements of support and positioning, and the reliability of the rotary compressor can be effectively ensured.

Referring to fig. 3, it can be understood that the length of the first oil blocking portion 324 is defined as L ₁ and the maximum length of the groove 323 is defined as L ₂ along the axial direction of the crankshaft 300, and the maximum length of the groove 323 is also the minimum length of the groove 323 since the sidewall is perpendicular to the central axis of the crankshaft 300. The method meets the following conditions: l ₁/L₂ is more than or equal to 0.25. It is easy to understand that the bearing surface of the side of the groove 323 on the crankshaft 300 is mainly an arc surface where the first oil blocking portion 324 is located. On the premise that the total length of the bearing part on the connecting section 320 is certain along the axial direction of the crankshaft 300, namely, on the premise that the value of (L ₁+L₂) is certain, when L ₁/L₂ is smaller than 0.25, the length of the groove body 323 is increased, the length of the first oil baffle part 324 is reduced, on the one hand, the area of the cambered surface where the first oil baffle part 324 is positioned is reduced, the bearing area of the side where the groove body 323 is positioned on the crankshaft 300 is reduced, the surface pressure is increased, and the thickness of an oil film at the position is reduced; on the other hand, the structural rigidity of the connection section 320 is lowered, the connection section 320 is easily deformed, the supporting force of the bearing body 400 to the connection section 320 is insufficient, the reliability of the rotary compressor is affected, and abnormal wear is caused.

Referring to fig. 9, it can be appreciated that, under the same operating condition, as the ratio L ₁/L₂ increases, the oil film thickness on the side of the crankshaft 300 where the groove 323 is located increases. When L ₁/L₂ is more than or equal to 0.25, the thickness of the oil film is kept at 1.6 mu m or more, and when L ₁/L₂ is less than 0.25, the thickness of the oil film is less than 1.6 mu m. Therefore, on the premise that the lubricity is increased by providing the groove 323, the length of the groove 323 is not excessively long, and the length of the first oil baffle portion 324 is relatively large, so that the thickness of an oil film on the side of the groove 323 on the crankshaft 300 is relatively large, good lubricity is maintained between the crankshaft 300 and the bearing body 400, and abrasion is reduced. At the same time, the structural rigidity of the connection section 320 can be ensured to meet the requirements of support and positioning, and the reliability of the rotary compressor can be effectively ensured.

Referring to FIG. 5, in other embodiments, it is understood that the groove 323 includes a bottom wall 326 and two side walls, the bottom wall 326 being straight and parallel to the central axis of the crankshaft 300. Along the circumference of the crankshaft 300, two ends of the bottom wall 326 respectively extend to the outer circumferential wall of the connecting section 320, namely, the bottom wall 326 is connected with the outer circumferential wall of the connecting section 320, and an edge is formed at the connection part of the bottom wall 326 and the outer circumferential wall of the connecting section 320 and is arranged along the axial direction of the crankshaft 300. Along the axial direction of the crankshaft 300, one side wall is connected to the lower end of the bottom wall 326, the other side wall is connected to the upper end of the bottom wall 326, and both side walls are perpendicular to the central axis of the crankshaft 300, i.e. the bottom wall 326 is closer to the central axis of the crankshaft 300 than the side walls, and the bottom wall 326 is rectangular. Therefore, the connecting section 320 forms the first oil blocking portion 324 at the upper end of the groove 323, forms the second oil blocking portion 325 at the lower end of the groove 323, and the first oil blocking portion 324 and the second oil blocking portion 325 protrude relative to the bottom wall 326, so that the upper and lower ends of the groove 323 do not penetrate the connecting section 320. The outer peripheral walls of the connecting section 320 at the first oil blocking portion 324 and the second oil blocking portion 325 are all complete cylindrical surfaces, and the connecting section 320 includes a shaft section where the groove 323 is located, a shaft section where the first oil blocking portion 324 is located, and a shaft section where the second oil blocking portion 325 is located.

On the premise of increasing lubricity by arranging the groove body 323, the bearing surface of the side of the groove body 323 on the crankshaft 300 along the radial direction of the crankshaft 300 comprises the cambered surface of the first oil blocking portion 324 and the cambered surface of the second oil blocking portion 325 due to the first oil blocking portion 324 and the second oil blocking portion 325, so that the bearing area of the side of the groove body 323 on the crankshaft 300 can be increased, the surface pressure is reduced, the thickness of an oil film at the position is increased, good lubricity between the crankshaft 300 and the bearing body 400 is kept, and abrasion is reduced. At this time, the lubricant flows downward through the gap between the outer circumferential wall of the connecting section 320 and the inner wall of the shaft hole 430 by gravity, so that the lubricant can flow, thereby taking away part of heat generated during the rotation of the crankshaft 300 by the lubricant.

Referring to fig. 2, it can be understood that the central oil hole 330 is closed toward one end of the bearing body 400, i.e., the upper end of the central oil hole 330 is closed, only the lower end is opened, and the central oil hole 330 is a blind hole. Therefore, the lubricating oil can only flow out of the central oil hole 330 through the first oil outlet 321, so that the lubricating oil cannot be sprayed to the top space of the crankshaft 300, the oil quantity reaching the top space of the crankshaft 300 is reduced, the oil discharge quantity of the rotary compressor is reduced, the oil level stability of an oil sump is maintained, and the reliability of the rotary compressor is improved. Meanwhile, the oil output of the first oil outlet 321 may be increased, thereby increasing the minimum oil film thickness between the crankshaft 300 and the bearing body 400, enhancing the lubrication effect, reducing wear, and further improving the reliability of the rotary compressor.

Referring to table 2, it is easy to understand that, in the third example, the central oil hole 330 penetrates through the connecting section 320 along the axial direction of the crankshaft 300, and the upper and lower ends of the groove 323 penetrate through the connecting section 320, and the oil discharge amount of the rotary compressor is 12%; in the fourth example, the upper end of the central oil hole 330 is closed, the lower end of the groove 323 penetrates the connecting section 320, and the upper end is provided with the first oil blocking portion 324, and at this time, the oil discharge amount of the rotary compressor is 10% and smaller than that of the third example. Therefore, the upper end of the central oil hole 330 is closed, and the first oil blocking portion 324 is provided at the upper end of the groove 323, so that the oil discharge amount of the rotary compressor can be effectively reduced, and the reliability of the rotary compressor can be improved.

Table 2: oil output ratio comparison under different schemes

Referring to fig. 6, in other embodiments, it may be appreciated that the connection section 320 is provided with a second oil outlet hole 322, the second oil outlet hole 322 is located at an end of the connection section 320 facing away from the motor assembly 200, a lower end of the second oil outlet hole 322 communicates with the central oil hole 330, an upper end (i.e., an oil outlet end) of the second oil outlet hole 322 is located at an upper end wall of the connection section 320, i.e., an oil outlet end of the second oil outlet hole 322 communicates with a head space of the crankshaft 300, and an inner diameter of the second oil outlet hole 322 is smaller than an inner diameter of the first oil outlet hole 321 and an inner diameter of the central oil hole 330. Therefore, the second oil outlet 322 having a smaller inner diameter is provided so as to penetrate the central oil hole 330 in the axial direction of the crankshaft 300, so that most of the lubricating oil in the central oil hole 330 flows out from the first oil outlet 321, and the oil output of the first oil outlet 321 can be increased, thereby increasing the minimum oil film thickness between the crankshaft 300 and the bearing body 400, enhancing the lubrication effect, reducing the wear, and further improving the reliability of the rotary compressor.

An embodiment of the second aspect of the present utility model provides a refrigeration appliance, which may be an electrical appliance such as an air conditioner, a refrigerator, or the like, including the rotary compressor of any of the above embodiments,

The refrigeration equipment adopts all the technical schemes of the rotary compressor of the embodiment, so that the refrigeration equipment has at least all the beneficial effects brought by the technical schemes of the embodiment.

The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, but the present utility model is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present utility model.

Claims

1. A rotary compressor, comprising:

The pump body assembly comprises a cylinder;

an electric machine assembly comprising a stator and a rotor, the stator being arranged around the rotor;

The crankshaft penetrates through the rotor and is connected with the rotor, the crankshaft comprises an eccentric part and a connecting section, the eccentric part and the connecting section are respectively positioned at two ends of the motor assembly along the axial direction of the crankshaft, the eccentric part is rotationally arranged in the cylinder, the crankshaft is provided with a central oil hole, the connecting section is provided with a first oil outlet, and the first oil outlet is communicated with the central oil hole;

The bearing body is provided with a shaft hole, and the bearing body is sleeved on the connecting section through the shaft hole;

The oil outlet end of the first oil outlet hole faces to a gap between the outer peripheral wall of the connecting section and the inner wall of the shaft hole.

2. The rotary compressor of claim 1, wherein: the first oil outlet holes are arranged along the radial direction of the crankshaft.

3. The rotary compressor according to claim 1 or 2, characterized in that: the outer peripheral wall of linkage segment is equipped with the cell body, the cell body with first oil outlet intercommunication, the cell body with inject the oil groove between the inner wall in shaft hole.

4. A rotary compressor according to claim 3, wherein: the groove body comprises a bottom wall and a side wall, the side wall is connected to one end of the bottom wall along the axial direction of the crankshaft, the bottom wall is closer to the central axis of the crankshaft than the side wall, and the two ends of the bottom wall along the circumferential direction of the crankshaft extend to the peripheral wall of the connecting section respectively.

5. The rotary compressor of claim 4, wherein: the bottom wall is a straight wall, the included angle between the reference plane passing through the central axis of the crankshaft and perpendicular to the bottom wall and the deflection direction of the eccentric part is theta, and the requirements are satisfied: θ is more than or equal to 45 degrees and less than or equal to 135 degrees.

6. The rotary compressor of claim 4, wherein: the maximum radial dimension of the connecting section is D, the maximum linear distance between two ends of the groove body in the circumferential direction of the crankshaft is W, and the requirements are met: W/D is less than or equal to 0.7.

7. The rotary compressor of claim 4, wherein: along the axial of bent axle, the cell body orientation motor element's one end runs through the linkage segment, the linkage segment includes first fender oil portion, first fender oil portion is located the other end of cell body.

8. The rotary compressor of claim 7, wherein: along the axial direction of bent axle, the length of first fender oil portion is L ₁, the maximum length of cell body is L ₂, satisfies: l ₁/L₂ is more than or equal to 0.25.

9. The rotary compressor of claim 4, wherein: the connecting section comprises a first oil blocking part and a second oil blocking part, and the first oil blocking part and the second oil blocking part are respectively positioned at two ends of the groove body along the axial direction of the crankshaft.

10. The rotary compressor of claim 1, wherein: the central oil hole is closed towards one end of the bearing body.

11. The rotary compressor of claim 1, wherein: the one end that the linkage segment deviates from motor element is equipped with the second oil outlet, the second oil outlet with the centre oilhole intercommunication, just the play oily end of second oil outlet is located the upper end wall of linkage segment, the internal diameter of second oil outlet is less than the internal diameter of first oil outlet and the internal diameter of centre oilhole.

12. Refrigeration device, characterized by comprising a rotary compressor according to any one of claims 1 to 11.